Means for stabilizing hydraulic controls



Sept. 19,- 1944.

.y MEANS FOR STABILIZING HYDRAULIC CONTROLS H, zlEBoLz 2,358,611

Filed June 5,-1941 2 Sheets-Sheet 1 REL/a y ivm VEL Mmmm;

Sept. 19, 1944. H. zlEBoLz 2,358,611

. MEANS FOR STABILIZING HYDRAULIC CONTROLS Filed June 5, 1941 2 Sheets-Sheet 2 Z9-5 y @T46 E W E O U TIME Patented Sept. 19, ,1944

"oFFlcE MEANS FORSTABILIZING HYDRAULIC CONTRO Herbert Ziebolz, Chicago, Ill.

,application June s, 1941, serial Nn. 396,712

6 Claims. (Cl. 13S-46) The present invention relates to a modulating valve for hydraulic controls.

The object of the invention is to provide a modulating valve betweena controlling iiuid relay having denite operating characteristics and 5 a servo-motor which controls a condition in response to changes in a condition, The purpose ofthe modulating valve is to modifythe operating characteristic; that is, the lrelation between the relay movement and the rate of servo-motor l0 travel in a predetermined manner. One of the l principal applications is in the field of fluid pressure operated controls wherein it is desirable or necessary. to increase the stability of control by modifying the rate of travel-of a' servo-motor so l5 that it becomes a definite function of the cono dition which is controlled.

It is a further ebieetfof the invention to pro-f vide modulating valve means in a iiuid relay sys- -tem having iiuid relay conduits connecting the 20 relay 'to operate a servo-motor and in which the valve means au tomatically .varies the rate of ow in both directions through the respective con-` duits to vary the rate of movement of the servomotor in proportion to changes in the relay po- 25 Another feature of the invention resides in providing 'a ydouble-acting modulating valve provided with oppositely disposed,varying re'stric\-\l tions so arranged that they are automatically .110

cleansed bythe fluid passing therethrough.

lFurther aims and advantages of the invention will appear inthe-specification in connection with the accompanying drawings, wherein:

Fig. 1 is a diagrammatic view illustrating a 35 -hyvdraulic control system with a modulating valve in one of the conduits;

' Fig. 2 is a longitudinal sectional view .of the modulating valve ot Fig. l;

Y, Fig. 3 is a cross section taken 'on line 3 3 of 4o Fig, 2 in the direction ofn the arrowsv Fig. 4 is a diagram showing the cylinder speed Figs. 5 to 8 are diagrammatic views illustrating a number of modied hydraulic control sys- 45 tems with modied modulating valves; and

Figs; 9 to 11 are control charts. Referring particularly to the drawings, the

illustrated embodiments of the invention will be explained as being applied to a iluidoperated 50.*

relay system wherein a servo-motor is employed to'controla condition, such as the flow o! gas, etc., in responseito condition changes, such as changes in pressure, fetc.

' It 1s a wen known rectum the si bility or 55 decreaseof rate of servo-motor travel. control is hunting, as shown in Fig: 9, it has fluid pressure actuated controls increases with If the 'travel directly proportional to condition changes'l 4 ,throughout the range of the relay movement.

It has, however, the great disadvantage that-due to thesmall openings vof the capillary tubes, the

danger of clogging is comparatively great and that capillary tubes are very sensitive to changes -of viscosity of the iluid. The xed restriction has the disadvantage that, as shown in Fig. 4, curve C, the effect is very pronounced at higher ratesv of servo-motor travel. As 'shown in Fig. 4, comparing curves A and C, assuming that curve A represents the relayl characteristicvvithout any restriction, curve C represents the rate of servomotor travel 'witha xed orice or adjustable valve in one of the control lines. It will be noted that there is practically nochange in rate of travel for smaller relay movements, while the resistance yincreases approximately with the square of the displacement or 1the rate of servomotor travel. Such a restriction therefore, de-

` ,creases the control speed when it is most needed and has very little effect in 'case of small variations or changes in the condition to be controlled. 'Ihe result usually, therefore, is the one shown in'Fig. 10, where a'certain'improvement is shown, as compared with Fig. 9. However, the

stability 'is not as yet satisfactory. Itis evident that it is desirable in many cases to have the rats of servo-motor travel which are small at small relay movements and are great f or maximum relay deections. This is obvious as such relay will give great stability in its neutral position. ,However, it will permit a fast movement of the servo-- motor in casces :of -sudden changes which mayv occur. The result of such characteristic as shown in curve B (Fig. 4), is shown in Fig. 11, which shows stable control. ,v

The ,invention solves theproblem by providing a variable restriction in one of the conduits to the servo-motorwhich changes the resistance to the ilow-of ilu'id to the servo-motor as a function of the'change of the condition, to pro uce the desired relay characteristic by the shape of the restriction.- 11n the illustrated embodiments, the design is such as to produce minimum uid openings for small changes in the condition and thus produce a maximum stability within any desired small range of displacements o! the relay. Also,

it 'provides a maximum opening for relatively large changes in the conditions.

In Fig. 1, the tube or conduit I2 has a iluid ilowf ing therethrough, such as air, a combustible gas, mixtures of gases, etc. which iluid ilow vis to be controlled by the throttle valve I3. The valve I3 'is adjusted by means of a piston I4 reciprocating in a cylinder I5 and -connected by suitable means I3 with the throttle valve. A conduit I1 is conynected to the...- conduit I'2 downstream of the Athrottle valve I3, and this conduit I1 is in communication with a pressure responsive device I3. The device I8 is provided with a ilexible dlaphragm I3 connected to' a uid jet pipe 20 of the well known Askania relay type by means of a lever.

Each hydraulic control system is provided with conduits 22 and 23 connected to opposite ends of' the cylinder I5 to convey the iluid means controlling the movement or adjustment of the piston I4. In one of the conduits 22 and'23, a modulatertures or slots 55 therein shown as converging inwardly toward the center or the valve 54. The conduits 23 and 53 terminate adjacent to the valve 54 and when the valve is in its neutral position it ing valve 24 is inserted in the controlling uid circuit which will be more fully described asto its functions in the following: f

Referring now to the specific structure of thev modulating valve shown in Figs. Zand 3, the cylindrical casing 25 consists of two chambers 26 and 21 each having elbow-pipe sections 28 and 23 respectively connected thereto and communieating with the respective chambers. A partition member is centrally secured in the casing 25 by means of a set screw 3l and consists of a central wall 32 with outer spaced walls 33, the latter each having a plurality of perforations 34 therein consisting of any suitable number and arranged in any desired order and spacing. The walls 32 and 33 'are provided with an aligned central bore 35 into which a valve member `36 is slidably mounted and which is in the form of a piston or needle valve havinga pair ,or set of part coneshaped grooves or variable apertures 31 of varying cross section with the base opening P3 at the outer end oi' each end of the valve and the pointed end 33 terminating in the central part of the valve adjacent the wall 32 when the valve is in its central or neutral position.

The ends 39 of the grooves or apertures are in spaced but overlapping relationship with each end 39 practically ush with one side of the wall 32 so that, when the valve is in its. neutral position, it has-a minimum free area for the ilow ofV fluid from one chamber 23 or 21 into the other through the grooves or apertures 31. Y

Each end of the valve member 33 has a -pointed section 43 seating or centered in a seat portion or p'in bearing 4I in the inner end of a compression coil spring 42 which, in turn, is supported on an adjustable abutment 43. The latter is mounted on a screw," threaded in the end closure 45 and provided with a protecting cap' 45 threaded on the screw and also acting as a locking member to maintain the desired compression A in the spring 42.

'I'he system shown in Fig. 1 is provided with a throttle valve 41 in conduit 23 and a second variable throttle valve 43 is arranged in a by-pass around the modulating valve 24. 'I'he jet-pipe relay is provided with the usual receiving oriilce pipes 49.

In the embodiment vshown in Fig. 5, the modulating valve is mechanically 'connected to a well known type of pilot which is mechanically operated in response to changes in a condition. In this instance, the operating iiuid under pressure is cuts ol! the flow of uid through both conduits 23 and 53 and thus prevents the operation of the servo-motor.

In the embodiment shown in Fig. 6, the'modulating valve is operated in response to the difierential pressure created by the relay system, this differential pressure being, in turn; a function of the change in the condition in line I2. Thedifapplied to two pressure responsive diaphragms which are held in their neutral position under the influence of springs. Any change inthe diilerential pressure moves the diaphragme and thereby changes the size of the restriction in one of the lines leading to the servo-motor. The modulating valve 24 of Fig. 6 also has a piston valve 54 with the part cone-shaped orvariable apertures or slots 55, but it is `actuated by bellows diaphragms 58 and opposing springs 51. Fig. 6 shows the parts in neutral position or4 in which no movement of the throttle valve I3 is taking place, the pressures'in conduits 22. and 23 being equal. `Any differential pressure, due to changes in pressure in conduit I2, will cause the valve to move proportional to the diilerential pressure and thus modifythe size of the valve restriction or opening.

In the'embodiment shown in Fig. '1, the restriction in one of the uid lines is varieddirectly in response to the pressure change in line I2, and, at the same time, the relay movement 20 is changed in response to the changes in pressure in line I2. In this instance, the pipe I1 is connected to a pipe 60 which latter is connected to a pressure responsive chamber 8l so that the iluid pressure will act on the diaphragm 32 to actuate the modulating valve 54.`

In the embodiment shown in Fig. 8, the restriction is changed as a function of the rat'e of ilows through one of the conduits to the servo-motor. A restriction is provided in `the conduit and a differential pressure responsive diaphragm which measures `the resistance which the restriction oiles to the flow of the controlling medium. The diaphragm, in turn, operates the'valve to change the size of the restriction in one of the fluid lines.

in this.instancethe pipe' z: is provided witna restriction 63 so that a differential pressure will delivered by a pipe 50 into a chamber-"5i and two 75 act on both sides of a diaphragm 34. which latter is connected to the modulating valve 54;

Equalizins springs 35 will restore the valve 54 to its closed .or non-active position.

It is obvious that in the systems disclosed the valves in one of the iiuid conduits will modify the pilot characteristics in such a `way that any relation between the change of the impulse, that is pilot movement. and the control speed can be obtained and thus the stability of the control is improved. l

In the valve and system of'Figs. 1 and 2, the oil enters one of the chambers 2l and 21 and, after passing through one of the apertured passages 3l, it enters the other chamber in the valve casing. A difference in pressure in pipes 2 2 and ferential pressure between conduits 22 and 23 is n partition 32.

' binations.

' dr'aulic control systems, comprising a casing, a

assacii 23 moves the piston I4 and as the pressure differential increases, the valve opens further and l thus permits an increased volume of uid to pass to the servo-motor and increases its speed accordingly. During this operation of the modulating valve 24, the valve member 36 is self-cleaning on each reversal of the piston I4. However, even if the tip ends of the passages 31 should become clogged, the result will be a greater differential pressure across the valve and thus cause the valve to open further.

In the system of Fig. 5, the variable orifice varies as a function of the pilot movement. The throttle valve 54, being attached to the pilot valve 52, the opening of the latter is a.` function of its displacement which varies the speed of piston I4.

In the system of Fig. 6, a pressure diiferential in the pipes 49 changes the position of the valve 54 to control the speed of the servo motor.l

In the systems of Figs. fl and 8, a diierential pressure in pipes 49 tends to move the piston I4 and, as soon as the piston moves, the modulating valve 54 in one of the oil conduits continues to move until the pressure drop decreases and is equal to the tension of the springs 65.

It is of course obvious that any desired number of apertures'or slots 3l may be provided in the valve member 36, which is likewise true of thev apertures or` slots 55 in the piston valve 54.- Also,

the apertures or slots 31 and 55 can comprise any 30 length and shape or configuration as for instance a square or rectangular cross section with flat or rounded internal ends instead of pointed ends and converging sides. The partition member 30, which may also be termed av sleeve, may comprise 35 a solid construction having Vfull and complete contacting surfaces with the valve member. The

sliding iit of the valve member 3B in the partition member or sleeve 30 may act as a capillary so that instead of pointed end grooves, such apertures 31 may have a side end portion whereby better results may be obtained under certain conditions and Arequirements wherein the-groove or aperture starts abruptly rather than pointed in which the capillary action of the pointed portion...is provided by the sliding fit of the piston valve in its sleeve. In such a construction of the -piston valve the actual starting or internal end portion of the grooves or apertures which are blunt rather than pointed. will underlap the sleeve and the sliding t thus performs the function of the pointed ends by capillary action.

It is also obvious that the pointed ends 39 cfg the grooves 31 may be shortened and made blunt 55 rather than' pointed so that the internal end of the grooves underlap the eiectiveedge of the Obviously, the present vinvention is not restrictedA to the particular embodiments shown and described. AMoreover, it is not indispensable that all the features oi' lthis invention be used conjointly, since they may be employed vadvantageously in various combinations and sub-com- I claim as my invention: Y 1. A modulating valve for a conduit of hypartition member in said casing dividing said 6o draulic systems, a valve member having a cylinmounted in said bore and having a plurality of apertures therein of which each aperture increases in size from zero to a maximum,l said valve member in its central position in the partition member lpermittinga minimum ilow between the two chambers through the apertures, each aperture'inthe valve member being part coneshaped with the apex of the cone adjacent the central part of the valve member and the partition member.

2. A modulating valve for a conduit of hydraulic control systems, comprising a casing, a partition member in said casing dividing said casing into two chambers, said member having-a bore therein, a valve member slidably mounted in said bore and having a plurality of apertures thereinl A closed position.

3. A modulating valve for a conduit of hydrau lic control systems,comprising a casing, a partition4 member in said casing dividing said casing into two chambers, said member having a bore therein, a valve member slidably mounted in said bore and having a plurality of apertures therein of which each aperture increases in size from zero to amaximum, said valve member in its central position in the partition member permittinga minimum flow betweeny the two chambers through the apertures, and an adjustable resilient device at each end of the casing and its respectiv end of the valve member to normally mamtain'the valve member in its central closed position. each adjustable resilient device including an abutment at the end of the casing and its respective end of the valve memberto normally maintain the valve member in its central closed f position.

4. A modulating valve according to claim 3, in which a screw member is provided threaded in the casing and contacting the abutment.

5. In a modulating valve for a conduit of hydrical configuration pointed at each end and having a pair of elongated apertures in the periphtion of the .valve member which provides the minimum opening for the valve member.

6. In a modulating valve for a conduit of hydraulic systems, a valve member having a pointed section at eachend thereof and' at least two elongated apertures in the peripheral surface thereof, eachaperture having its greatest opening adjacent the pointed section and converging vto a point toward the central portion of the valve member, said pointed ends of the apertures providing a minimum free area for the valve members.

HERBERT zrEBoLz.

a bore therein, and a valvemember slidablyQ 

